US20090193817A1 - Method for refrigerating a thermal load - Google Patents

Method for refrigerating a thermal load Download PDF

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Publication number
US20090193817A1
US20090193817A1 US11/915,934 US91593406A US2009193817A1 US 20090193817 A1 US20090193817 A1 US 20090193817A1 US 91593406 A US91593406 A US 91593406A US 2009193817 A1 US2009193817 A1 US 2009193817A1
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US
United States
Prior art keywords
evaporator
source
storage tank
refrigeration
fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US11/915,934
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English (en)
Inventor
Jean-Pierre Germain
Didier Alo
Jean-Yves Thonnelier
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
Original Assignee
LAir Liquide SA a Directoire et Conseil de Surveillance pour lEtude et lExploitation des Procedes Georges Claude
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by LAir Liquide SA a Directoire et Conseil de Surveillance pour lEtude et lExploitation des Procedes Georges Claude filed Critical LAir Liquide SA a Directoire et Conseil de Surveillance pour lEtude et lExploitation des Procedes Georges Claude
Assigned to L'AIR LIQUIDE SOCIETE ANONYME POUR L'ETUDE ET L'EXPLOITATION DES PROCEDES GEORGES CLAUDE reassignment L'AIR LIQUIDE SOCIETE ANONYME POUR L'ETUDE ET L'EXPLOITATION DES PROCEDES GEORGES CLAUDE ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ALO, DIDIER, GERMAIN, JEAN-PIERRE, THONNELIER, JEAN-YVES
Publication of US20090193817A1 publication Critical patent/US20090193817A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D16/00—Devices using a combination of a cooling mode associated with refrigerating machinery with a cooling mode not associated with refrigerating machinery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D3/00—Devices using other cold materials; Devices using cold-storage bodies
    • F25D3/10—Devices using other cold materials; Devices using cold-storage bodies using liquefied gases, e.g. liquid air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit

Definitions

  • the present invention relates to the field of refrigeration, particularly of the mechanical type and the cryogenic type, and is concerned in particular with applications in the field of the treatment of food products, such as deep freezing and freezing.
  • CO 2 can also be employed as a two-phase refrigerant in association with a compression cycle using a refrigerant such as ammonia.
  • the new generations of cascade system comprise two distinct compression units:
  • cryogenic refrigeration system generally means a system producing refrigeration brought about by a change of phase of a cryogenic fluid in an open circuit.
  • manufacturers who have opted for a mechanical refrigeration system could, during a given period, use the deep freezer with a cryogenic cold source, which would in particular have the advantage of improving the spreading of the investments during the period of launching of the frozen product on the market.
  • the final “desired” refrigeration action may be due to mechanical refrigeration and cryogenic refrigeration or due to only one of the two systems.
  • the system which does not directly contribute to the “desired” refrigeration action is used to enable the other system to operate under extended conditions (power, temperature).
  • the “consumable” cryogenic fluid is CO 2 and is mixed with the fluid of the mechanical system which feeds the evaporator of the installation using the cold source to cool a thermal load.
  • the latter fluid is also CO 2 , both for the “recycled” refrigerant and the refrigerating fluid. This additional CO 2 injection takes place before producing refrigeration in the evaporator.
  • the fluid of the mechanical refrigeration circuit having to remain at constant weight, it is necessary for the quantity of original cryogenic CO 2 injected to be removed from the network after having been vaporized. As shown below, this extraction of CO 2 vapor can be carried out at various locations of the circuit.
  • the proposed solution consists in mixing the fluids issuing from an open circuit using CO 2 as cryogenic fluid and from a closed circuit using CO 2 as a refrigerant or as a refrigerating fluid.
  • the present invention relates to a method for refrigerating one or more thermal loads whereby a first CO 2 source is provided from a mechanical refrigeration system, and in which one or more evaporators is fed from said first source to cause the evaporation of the CO 2 and thereby cool said one or more thermal loads, and is characterized in that a second CO 2 source, consisting of a cryogenic CO 2 storage unit, is provided and in that there is an influx of CO 2 from said second source, so that the flow of fluid fed to the evaporator(s) is a mixture of liquid CO 2 issuing from said first source and liquid CO 2 issuing from said second source.
  • Method for refrigerating one or more thermal loads whereby a first CO 2 source is provided from a mechanical refrigeration system, and in which one or more evaporators is fed from said first source to cause the evaporation of the CO 2 and thereby cool said one or more thermal loads,
  • a second CO 2 source consisting of a cryogenic CO 2 storage unit, is provided and in that there is an influx of CO 2 from said second source, so that the flow of fluid fed to the evaporator(s) is a mixture of liquid CO 2 issuing from said first source and liquid CO 2 issuing from said second source.
  • the mechanical refrigeration system carries out the steps of:
  • a quantity of CO 2 substantially equivalent to that corresponding to said influx of CO 2 is removed to the exterior by one or a combination of the following methods:
  • the fluid or part of the fluid obtained at the outlet of the evaporator(s) is sent to a storage tank and said CO 2 stream to be removed to the exterior is extracted and removed from said tank;
  • part of the fluid obtained at the outlet of the evaporator(s) is separated and removed to the exterior, the remainder being sent either to said storage tank, or to a step of condensation by a cold source provided by a vapor compression system and the liquid thereby condensed is then stored in the storage tank;
  • the quantity of CO 2 present in the circuit is comprised between two predefined operating limits.
  • the important factor is to ensure that the quantity of CO 2 present in the circuit does not increase endlessly in an uncontrolled manner (due to the influx of original cryogenic CO 2 ), which would be inconceivable, quite on the contrary the quantity of CO 2 present in the circuit remains substantially constant or in any case remains comprised between two acceptable and predefined operating limits.
  • a quantity of CO 2 substantially equivalent to that which has been admitted into the circuit and which was of cryogenic origin must therefore be removed to the exterior of the circuit.
  • the useful refrigeration is produced by the evaporation of a stream of CO 2 issuing from the mixture of a flow from a cryogenic CO 2 storage unit and a flow of CO 2 obtained by a mechanical system.
  • the “total” CO 2 flow produces the useful refrigeration in an evaporator located in the installation using the refrigeration to cool a load.
  • the total CO 2 flow is separated into two streams, one substantially equal to the flow from the cryogenic storage unit, and the other equal to the flow originating from the mechanical refrigeration.
  • the flow of mixed cryogenic CO 2 and the flow of separated CO 2 are controlled respectively by opening a feed valve from the storage unit and by opening the CO 2 extraction valve.
  • These valves are controlled for example:
  • the flow which substantially corresponds to the one from the cryogenic storage unit is removed directly to the atmosphere or indirectly by passing through an oil separation phase if necessary.
  • the coupling of the two circuits can be achieved in various ways, and particularly:
  • the two CO 2 streams can be mixed:
  • the two CO 2 streams can be mixed:
  • the coupling of the two circuits must be controlled so that the quantity of CO 2 present in the closed circuit remains substantially constant or remains at least comprised between two acceptable operating limits.
  • the flow of mixed cryogenic CO 2 and the flow of separated CO 2 are controlled respectively, for example, by opening a feed valve from the storage unit and by opening the CO 2 extraction valve.
  • These valves can be controlled for example either:
  • FIG. 1 is a schematic representation of an exemplary mechanical refrigeration system (two compression units);
  • FIG. 2 is a schematic representation of a cryogenic refrigeration system
  • FIG. 3 is a schematic representation of an installation suitable for implementing the invention.
  • FIG. 4 is a schematic representation of a second installation suitable for implementing the invention (mixing of the fluids issuing from the open circuit using CO 2 as cryogenic fluid and the closed circuit also using CO 2 as refrigerating fluid);
  • FIG. 5 is a schematic representation of a third installation suitable for implementing the invention.
  • FIG. 6 is a schematic representation of a fourth installation suitable for implementing the invention.
  • FIG. 1 shows the following elements:
  • the thermal load to be cooled ( 1 ) is cooled by a vapor compression cycle cascaded at low temperature with CO 2 as refrigerant.
  • the advantage of a cascade is to obtain a high energy efficiency when the total temperature difference between the low temperature evaporator and the high temperature condenser is high.
  • the CO 2 evaporation temperature is adjusted for the use of the cooling required between ⁇ 56° C. and ⁇ 10° C.
  • the heat exchange between the CO 2 condenser and the evaporation of the high pressure circuit takes place at an optimized temperature depending on the refrigerant of the high temperature circuit and the total temperature difference, and is generally between ⁇ 28° C. and ⁇ 5° C.
  • the CO 2 in the low temperature circuit flows in a closed circuit.
  • FIG. 2 shows the following elements:
  • a pressure-reducing member causing the CO 2 to go from the storage pressure to the operating pressure in the evaporator, i.e. typically between 5.2 bar and 26.5 bar and preferably between 5.5 bar and 10 bar.
  • the CO 2 tank serves to feed one or more evaporators for cooling the thermal load or loads.
  • the flow(s) are controlled according to a temperature or a pressure.
  • the CO 2 evaporates in one or more evaporators between ⁇ 56° C. and ⁇ 10° C.
  • the vaporized CO 2 is discharged to the atmosphere via an exhaust duct.
  • FIG. 3 is a schematic representation of one of the embodiments of the present invention.
  • the thermal load or loads are cooled by the evaporation of the CO 2 in one or more evaporators 2 .
  • the liquid CO 2 fed to the evaporator(s) is supplied with a cascaded vapor compression system 31 comparable to the one described in connection with FIG. 1 , and with a cryogenic CO 2 storage unit 32 .
  • the two liquid CO 2 supply means are connected in the storage tank 3 of the low temperature circuit of the cascaded system where the two CO 2 streams are mixed.
  • the CO 2 issuing from the condensation of the low temperature circuit is expanded in the member 11 and accumulates in the tank 3 .
  • the CO 2 from the cryogenic storage unit is flow-controlled by the valve 21 and is expanded by the member 22 to the pressure of the tank 3 .
  • the circulating pump 4 serves to feed the evaporator(s) cooling the thermal load(s).
  • the pump must be dimensioned to circulate a flow equal to the sum of the CO 2 streams supplied by the cryogenic storage unit 32 and the low pressure compression circuit 7 .
  • the additional refrigerating capacity is supplied by the CO 2 stream from the cryogenic storage unit 32 .
  • the quantity of CO 2 injected into the tank 3 must be removed after evaporation of the liquid via an extraction circuit 33 .
  • the CO 2 flow supplied by the storage unit 32 can provide from 0 to 100% of the refrigerating capacity associated with the thermal load(s).
  • the CO 2 from the storage unit serves to supplement the refrigerating capacity of the compression system during production peaks in order to avoid oversizing said compression system.
  • the CO 2 from the cryogenic storage unit can supply 100% of the refrigerating needs, thereby avoiding the shutdown of production.
  • the operating pressures and temperatures of the cascaded compression system and of the cryogenic storage unit are, for example, comparable to those already indicated with reference to FIGS. 1 and 2 above.
  • FIG. 4 shows another exemplary embodiment of the invention.
  • the thermal load or loads are cooled by one or more evaporators 2 using CO 2 .
  • the liquid CO 2 is supplied, on the one hand, by the liquefaction of all or part of the CO 2 vapors issuing from the evaporator(s) 2 , condensation carried out in the heat exchanger 41 , and on the other, by the CO 2 issuing from the cryogenic storage unit.
  • the CO 2 flowing through the evaporator(s) and the condenser 41 is called the “refrigerating” fluid.
  • a refrigeration system 40 (compression system using CO 2 or other refrigerants in a cascade or not) serves for liquefying the CO 2 from one or more evaporators 2 .
  • the liquefaction of the CO 2 can take place in a heat exchanger distinct from the storage tank 3 (as is the case in this FIG. 4 ) or in this tank via a heat exchanger (as is the case in connection with FIG. 6 ).
  • a refrigerating circuit serves to split the compression system, which may be installed in a technical room separate from the installation cooling the thermal load.
  • a reserve 3 allows the mixing of the two CO 2 streams and two extraction lines 42 serve to extract a quantity of CO 2 equal to that issuing from the cryogenic storage unit and to remove it to the external ambient air. This extraction is carried out downstream of the evaporator 2 (on the line returning to the tank 3 ) and/or directly on the tank 3 . The latter case forces the condenser 41 to avoid completely condensing the CO 2 stream.
  • the compression system producing the refrigerating action for completely or partially cooling the thermal load consists of the compressor 56 , a condenser 57 , and a high pressure tank 58 , a pressure-reducing member 54 and one (or more) evaporator(s) 50 .
  • the refrigerant is CO 2 .
  • the cryogenic storage unit of CO 2 51 is connected to the storage tank 58 via a line equipped with a flow control valve 32 and a pressure-reducing member 53 .
  • the CO 2 is mixed with that of the compression system in the tank 58 .
  • the CO 2 from the cryogenic storage unit providing from 0 to 100% of the refrigerating needs, but is preferably used to supplement the refrigerating capacity of the compression system during production peaks or the shutdown thereof.
  • the CO 2 from the cryogenic storage unit is partially vaporized by expansion in the member 53 .
  • the vapor is removed from the tank 58 by an extraction line 59 .
  • the liquid CO 2 accumulated in the tank 58 is expanded in the pressure-reducing member 54 and is evaporated in the evaporator 50 .
  • a CO 2 vapor extraction unit ( 55 ) is installed to discharge the CO 2 introduced by the cryogenic storage unit.
  • the extractions 55 and 59 are adjusted so that the quantity of CO 2 extracted is equal to the quantity of CO 2 introduced by the cryogenic storage unit.
  • the condenser 57 is cooled by a compression system forming a cascade as explained for FIG. 3 and not described again here.
  • one of the main differences between the embodiment in FIG. 3 and that in FIG. 5 resides in the position of the CO 2 storage tank, which may be at low pressure ( FIG. 3 ) or at high pressure ( FIG. 5 ) of the CO 2 compression system. If the device in FIG. 3 is advantageous for simplifying the control of the extraction of CO 2 , the device in FIG. 5 serves to avoid the distribution pump.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Carbon And Carbon Compounds (AREA)
US11/915,934 2005-06-02 2006-05-18 Method for refrigerating a thermal load Abandoned US20090193817A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR0551475 2005-06-02
FR0551475A FR2886719B1 (fr) 2005-06-02 2005-06-02 Procede de refrigeration d'une charge thermique
PCT/FR2006/050460 WO2006129034A2 (fr) 2005-06-02 2006-05-18 Procede de refrigeration d'une charge thermique

Publications (1)

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US20090193817A1 true US20090193817A1 (en) 2009-08-06

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US11/915,934 Abandoned US20090193817A1 (en) 2005-06-02 2006-05-18 Method for refrigerating a thermal load

Country Status (4)

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US (1) US20090193817A1 (de)
EP (1) EP1902263A2 (de)
FR (1) FR2886719B1 (de)
WO (1) WO2006129034A2 (de)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120048881A1 (en) * 2010-08-25 2012-03-01 Paul Drube Bulk liquid cooling and pressurized dispensing system and method
US20120291480A1 (en) * 2011-05-18 2012-11-22 Girard John M Liquid carbon dioxide refrigeration system
JP2013002737A (ja) * 2011-06-16 2013-01-07 Mitsubishi Electric Corp 冷凍サイクル装置
FR2979336A1 (fr) * 2011-08-31 2013-03-01 Cryo Net Procede et installation de production de dioxyde de carbone sous forme solide.
US20130192275A1 (en) * 2011-07-22 2013-08-01 Lockheed Martin Corporation Idca for fast cooldown and extended operating time
US9207540B1 (en) 2014-05-30 2015-12-08 Lockheed Martin Corporation Integrating functional and fluidic circuits in joule-thomson microcoolers
CN106091459A (zh) * 2016-06-06 2016-11-09 济南欧菲特制冷设备有限公司 一种一体式载冷系统机组
US9813644B1 (en) 2014-06-19 2017-11-07 Lockheed Martin Corporation Nano-antenna array infrared imager
US9869429B2 (en) 2010-08-25 2018-01-16 Chart Industries, Inc. Bulk cryogenic liquid pressurized dispensing system and method
US9999885B1 (en) 2014-05-30 2018-06-19 Lockheed Martin Corporation Integrated functional and fluidic circuits in Joule-Thompson microcoolers
WO2019147563A1 (en) * 2018-01-23 2019-08-01 The Tisdale Group Liquid nitrogen-based cooling system
US11137172B2 (en) * 2016-07-26 2021-10-05 Efficient Energy Gmbh Heat pump system having heat pump assemblies coupled on the input side and output side
US20230023822A1 (en) * 2021-07-20 2023-01-26 John A. Corey Dual-mode ultralow and/or cryogenic temperature storage device

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2915559B1 (fr) * 2007-04-25 2012-10-26 Air Liquide Systeme de secours de refroidissement au co2
FR2956730B1 (fr) * 2010-02-25 2012-04-06 Air Liquide Procede de refroidissement cryogenique utilisant un ecoulement de co2 diphasique solide-gaz
FR2960952B1 (fr) * 2010-06-03 2012-07-13 Air Liquide Procede et installation de refroidissement cryogenique utilisant du co2 liquide mettant en oeuvre deux echangeurs en serie
FR3013647B1 (fr) * 2013-11-25 2016-01-01 Air Liquide Systeme frigorifique cryo-mecanique mettant en œuvre des echanges cryogene/frigorigene
FR3089603B1 (fr) * 2018-12-06 2023-03-31 Beg Ingenierie Installation de réfrigération

Citations (3)

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Publication number Priority date Publication date Assignee Title
US1408453A (en) * 1921-01-24 1922-03-07 Justus C Goosmann Refrigerating apparatus
US4127008A (en) * 1976-11-01 1978-11-28 Lewis Tyree Jr Method and apparatus for cooling material using liquid CO2
US5042262A (en) * 1990-05-08 1991-08-27 Liquid Carbonic Corporation Food freezer

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Publication number Priority date Publication date Assignee Title
DE10109236A1 (de) * 2001-02-26 2002-09-05 Joerg Fuhrmann CO¶2¶-Kälteanlage
JP4070583B2 (ja) * 2002-11-14 2008-04-02 大阪瓦斯株式会社 圧縮式ヒートポンプシステム
EP1422487A3 (de) * 2002-11-21 2008-02-13 York Refrigeration APS Heissgasabtau für Kälteanlagen
FR2847664B1 (fr) * 2002-11-25 2005-12-02 Dispositif compensant les fuites d'un circuit de climatisation automobile ou de refrigeration de vehicule frigorifique utilisant du dioxyde de carbone comme fluide frogorigene

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1408453A (en) * 1921-01-24 1922-03-07 Justus C Goosmann Refrigerating apparatus
US4127008A (en) * 1976-11-01 1978-11-28 Lewis Tyree Jr Method and apparatus for cooling material using liquid CO2
US5042262A (en) * 1990-05-08 1991-08-27 Liquid Carbonic Corporation Food freezer

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9869429B2 (en) 2010-08-25 2018-01-16 Chart Industries, Inc. Bulk cryogenic liquid pressurized dispensing system and method
US9939109B2 (en) * 2010-08-25 2018-04-10 Chart Inc. Bulk liquid cooling and pressurized dispensing system and method
US20120048881A1 (en) * 2010-08-25 2012-03-01 Paul Drube Bulk liquid cooling and pressurized dispensing system and method
US20120291480A1 (en) * 2011-05-18 2012-11-22 Girard John M Liquid carbon dioxide refrigeration system
JP2013002737A (ja) * 2011-06-16 2013-01-07 Mitsubishi Electric Corp 冷凍サイクル装置
US20130192275A1 (en) * 2011-07-22 2013-08-01 Lockheed Martin Corporation Idca for fast cooldown and extended operating time
US9328943B2 (en) * 2011-07-22 2016-05-03 Lockheed Martin Corporation IDCA for fast cooldown and extended operating time
EP2758728A4 (de) * 2011-07-22 2015-02-18 Lockheed Corp Idca für schnellere abklingzeit und längere betriebszeit
EP2758728A1 (de) * 2011-07-22 2014-07-30 Lockheed Martin Corporation Idca für schnellere abklingzeit und längere betriebszeit
FR2979336A1 (fr) * 2011-08-31 2013-03-01 Cryo Net Procede et installation de production de dioxyde de carbone sous forme solide.
US9999885B1 (en) 2014-05-30 2018-06-19 Lockheed Martin Corporation Integrated functional and fluidic circuits in Joule-Thompson microcoolers
US9207540B1 (en) 2014-05-30 2015-12-08 Lockheed Martin Corporation Integrating functional and fluidic circuits in joule-thomson microcoolers
US9813644B1 (en) 2014-06-19 2017-11-07 Lockheed Martin Corporation Nano-antenna array infrared imager
CN106091459A (zh) * 2016-06-06 2016-11-09 济南欧菲特制冷设备有限公司 一种一体式载冷系统机组
US11137172B2 (en) * 2016-07-26 2021-10-05 Efficient Energy Gmbh Heat pump system having heat pump assemblies coupled on the input side and output side
WO2019147563A1 (en) * 2018-01-23 2019-08-01 The Tisdale Group Liquid nitrogen-based cooling system
US11306957B2 (en) 2018-01-23 2022-04-19 The Tisdale Group, LLC Liquid nitrogen-based cooling system
US20230023822A1 (en) * 2021-07-20 2023-01-26 John A. Corey Dual-mode ultralow and/or cryogenic temperature storage device
US11867446B2 (en) * 2021-07-20 2024-01-09 John A. Corey Dual-mode ultralow and/or cryogenic temperature storage device

Also Published As

Publication number Publication date
FR2886719B1 (fr) 2007-08-10
WO2006129034A3 (fr) 2007-10-11
FR2886719A1 (fr) 2006-12-08
EP1902263A2 (de) 2008-03-26
WO2006129034A2 (fr) 2006-12-07

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